High-speed reset counter



Dec. 25, 1962 JJJ. AMBROZAlTlS 3,070,300

HIGH-SPEED RESET COUNTER Filed Sept. 26, 1958 FIG. I

4 Sheets-Sheet 1 FIG. 2

INVENTOR. JOHN J. AMBROZAITIS ATTORNEYS Dec. 2 5, 1962 J. J. AMBROZAITIS HIGH-SPEED RESET COUNTER 4 Sheets-Sheet 2 Filed Sept. 26, 1958 FIG. 3

FIG. 5

INVENTOR JOHN J. AMBROZAITIS BY HI f ZTTORNEYS //V W/Al' 2 J. J. AMBRozAms 3,070,300

HIGH-SPEED RESET COUNTER Filed Sept. 26, 1958 4 Sheets-Sheet 4 INVENTOR. JOHN J. AMBROZAITIS BY MCTW, @7016, my

ATTORNEYS United States Patent Ofifice 3,07%,30b Patented Dec. 25, 1982 The present invention relates to counters, and more particularly to certain improvements in counter mechanisms incorporating a plurality of counting drums.

Although the present invention is not necessarily so restricted, it is particularly applicable for use in timing device, where a counting mechanism, driven by a constant speed motor, for example, registers elapsed time or time intervals. One of the specific features of the invention resides in the provision in a counting mechanism utilizing Geneva-type mechanisms for effecting transfer between registers, of a novel and improved means for quickly resetting the counting mechanism to Zero after a counting operation. In this respect, when the counting device is employed as a timer, for example, the counting mechanism may be caused to move in an advancing direction during the measurement of a relatively substantial interval of time (i.e., one hundred seconds) and under circumstances in which rewin-ding the counter to zero would require too much time. Accordingly, a simplified but highly effective arrangement is provided for resetting all of a plurality of counting drums to zero within an interval of time which is not substantially in excess of the time required to efiect a single revolution of the fastest counting drum. The improved arrangement includes a novel means for simultaneously disengaging the various drums from the respective transfer mechanisms and from the main drive mechanism and bringing into operation stop means for engaging the respective drums as they are returned to zero positions. The several drums are mounted on a single drive shaft, in a manner providing limited running friction between the drums and means fixed to the shaft, so that, when the main drive means and transfer means are disconnected, the drums tend to rotate with the drive shaft and are returned thereby to their zero or starting positions within approximately a single revolution of the shaft.

Another specific feature of the invention resides in the provision, in a counting device (e.g. of the tenstransfer type) having Geneva-type transfer elements interconnecting drums of ascending order, of means operative when the transfer elements are disengaged for effecting resetting of the drums to Zero positions, to orient the respective transfer elements appropriately for re-engagement with the respective drums after rese'. Advantageousiy, the transfer elements are gears which interconnect the drums each with a drum of the higher order. The transfer gear ar carried by a shaft which is moved away from the counting drums during reset, and means are provided for engaging the transfer gears during the reset period and effecting the appropriate rotational orientation thereof prior to re-engagement of the transfer gears with the reset drums.

One of the important features of the invention resides in the provision, in a counting device of the type described, of novel line-up means, effective at the end of a counting operation, to rotate the lowest order drum from any position between nine and zero index positions, for ex ample, to the closer one of the two positions. Thus, in a tens-transfer counter, a drum of a higher order is caused to move from one index position to another during the interval in which the drum of the next lower order moves between its nine and zero index positions. At all other times, drums of the higher orders are stationary.

Accordingly, on each occasion when the drum of the lowest order is stopped between the nine and zero index positions, one or more drums of the higher orders necessarily will be stopped between index positions. In accordance with the present invention, reading of the counter drums at the end of a counting or timing interval is facilitated greatly by the provision of means acting on the drum of the lowest order and effective to rotate the drum ahead to the zero index position or back to the nine index position on any occasion when the drum stops between those positions. The line-up is effected substantially instantaneously, at the end of the counting or timing interval, and all of the higher order drums of the counter are thus properly aligned in appropriate viewing windows.

A further specific feature of the invention resides in the provision of a simplified means operating in conjunction with the line-up means and cficctive immediately at the end of a counting or timing interval for engaging and frictionally retaining one or more of the drums of the counter, advantageously the drum of the highest order, so that the positions of the drums are held fixed, for convenient reading, even under conditions in which the counter is subject to substantial vibrations.

For a better understanding of the invention, and for a further discussion of various advantageous features thereof, reference should be made to the following detailed description and to the accompanying drawings, in which:

FIG. 1 is a fragmentary, longitudinal, cross-sectional view of a high speed reset timing device incorporating the improved features of the invention, the cross-sectional view being taken as on line 1-4. of FIG. 6;

PEG. 2 is a fragmentary, side elevational view of the timer of FIG. 1, with the cover removed;

3 is a cross-sectional View, as taken generally along line 3-3 of FIG. 2;

FiG. 4 is a fragmentary, cross-sectional view illustrating the operation of mechanism shown in FIG. 3;

HG. 5 is a fragmentary, cross-sectional view taken generally along line 5--5 of FIG. 1;

FIG. 6 is a cross-sectional view taken generally along line s s of PEG. 1 and illustrating a front view of the counter mechanism;

FIG. 7 is a simplified, cross-sectional view, similar to PEG. 5, illustrating the operation of the counting mechanism during a counting or timing interval;

FIGS. 8 and 9 are-simplified, cross-sectional views, similar to FIG. 7, illustrating the sequence of operations for efiecting line-up of the drums at the end of a timing interval;

Fit}. 10 is a simplified, cross-sectional view, similar to FIG. 7, illustrating the apparatus toward the end of reset;

FIG. 11 is a front view of the timer assembled in its casing;

FIG. 12 is a simplified, schematic representation of a control circuit used in connection with the operation of the improved timer; and

FIG. 13 is a fragmentary, cross-sectional view of a modified form of line-up means which may be used in the timer of FIG. 1.

Referring now to the drawings, the reference numeral 19 designates generally a high speed, motor driven timer incorporating features of the invention and including a frame of conventional construction, comprising one or more decks 11 and a plurality of longitudinally disposed spacer posts 12. At the outer or forward end of the timer unit, a counter frame 13 is secured by its base 14 to outer ends of the spacer posts 12 and has spaced arms 15, in extending longitudinally outward from the base. Advantageously, the counter frame 13 may be of die-cast acres-co construction, although one of the arms thereof may be secured by screws 17 to a frame bracket 18 to facilitate assembly and disassembly.

Journaled in the arms of the counter frame is a drive shaft 39 which mounts, between its ends, a plurality of counter drums 2tl23. By means of suitable spacing collars or bushings (not specifically identified) and retaining rings R, the drums 2tl23 are held in desired axial relation on the drive shaft 19. In accordance with the invention, the drum are rotatable on the drive shaft but are facially frictionally engaged by retaining rings R which are fixed to the shaft whereby relative rotation between the shaft and drums is frictionally restrained to a limited degree. At one end, the drive shaft 19 mounts a bevel gear 24 which engages a similar bevel gear 25 fixed to the end of an input shaft 26 jo-urnaled in a bracket 27 on the counter frame and forming part of an input drive to be described in greater detail. At its opposite end, the drive shaft 19 mounts a pair of pinions 255, 29, which are advantageously of identical shape and size and, in accordance with the invention, one of the pinions, 28, is fixed to the drive shaft while the other pinion, 29, i rotatable on the shaft but is fixed to the adjacent drum forming the lowest order drum of the counting mechanisrn.

The counting mechanism is, in its general operation, of a conventional tens-transfer type, in which drums of a lower order are connected each to a drum of a higher order. Thus, a plurality of transfer gears 3tl32 are mounted for free rotation on a spindle shaft 33 supported at its ends in a rocker frame 34 to be described in more detail. Each transfer gear includes a first portion constituting a pinion of conventional form, which engages a gear fixed to a drum of a higher order, and a second portion which forms an element of a Geneva-type mechanism (advantageously, a pinion similar to the first portion but with alternate teeth removed) adapted for cooperation with an element of the mechanism carried by a lower order drum. During a complete revolution of the lowest order drum 2%), for example, the drum holds the transfer gear motionless during its traverse from a Zero index position to a nine index position and then engages and rotates the gear through a predetermined angle as the drum rotates from a nine index position to a zero index position. The rotation of the transfer gear 30, during this limited interval, is such that the drum 21 of the next higher order is rotated from one index position to another. The operation of the other drum is, of course, similar so that each revolution of a drum of a lower order effects movement of a drum f the next higher order through one index position during the interval of movement of the lower order drum between nine and zero index positions.

Operation of the counting mechanism is effected by driving of the drum 2%) of the lowest order, and this is accomplished, in accordance with the invention, by means of a transmission gear 35 mounted for rotation on the spindle shaft 33. The transmission gear 35, in its operative position, engages the pinions 28, 29 on the drive shaft 19. Accordingly, rotation of the shaft and the pinion 28 affixed thereto causes the transmission gear 35 to rotate and thereby effects the desired rotation of the pinion 29. Thus, as will be understood, when the transmission gear 35 is in its operative position, as shown in FIG. 1, for example, the gears or pinions 2S, 2% are effectively locked together for rotation in unison. The drum 21) of the lowest order, which is afiixed to the pinion 29, will thus rotate along with the drive shaft 19, and rotation of the drums 212.3 of higher orders is effected through the transfer gears Bill-32 in the manner described.

The respective drums 2tl..3 have suitable indicia on their outer surfaces, such as circumferentially spaced numerals, from zero to nine, and the drum 2d of the lowest order may additionally be provided with appropriate calibrations between the index numerals. A suitable face plate 36 is conveniently secured to the end of the counter frame 13 and is provided with a plurality of viewing windows 37, through which limited portions of the counting drums are visible from-the front of the mechanism, substantially as indicated in FIG. 11. The drums are not provided with calibrations between index positions, as the movement of the upper order drums takes place in increments of one index position, while movement of lowest order drum is continuous.

in the normal operation of a counting device of the tvpe herein described, the lowest order drum 2% may, at the end of a counting or timing interval, lie between its nine and zero index positions, wherein indexing movement of one or more of the higher order drums is taking place. And, if the drums are held in such positions, the index numerals thereon will be improperly aligned with the viewing windows 37, so that rapid and accurate ascertainment of the numerals is difficult. Accordingly, as one of the important features of the invention, means are pro vided for acting upon the drum Ztl of the lowest order, at the end of each operation, for moving the drum from any position between its nine and zero index positions {i.e., where the numerals 9 and 0 are partly exposed in the window 37) to the closer of the two index positions. To this end, a cam 38 is affixed to the lowest order drum and is provided with a pointed lobe 29, visible in FiGS. 7-10, for example. in the first illustrated form f the invention, the cam 38 may be generally circular, except for the pointed, projecting lobe 39, and is advantageously provided at each side of the lobe 39 with small recesses or indentations 49. The cam 38 is adapted for cooperation with a cam follower 41, in the form of a roller carried at the end of a line-up arm 42. The line-up arm 42 is fixed to a shaft 43 and is adapted for limited rotational movement with the shaft.

The operation of the line-up means is illustrated gcnorally in PRES. 8 9, and is as follows: When the drum of the lowest order stops in an index position between 9 ans 0, the pointed looe of the cam 38 lies opposite the follower at, which normally is held away from the cam. immediately following the timing or counting interval, the line-up arm is moved toward the cam, by rotation of the shaft 43, so that the cam follower 41 engages the lobe 39 and causes the drum 26 to rotate in one direction or the other, to either the nine or the zero index position, depending upon which is closer. In this respect, it will be understood that the point of the cam lobe 39 is so positioned, with respect to the drum, as to cause the drum 2b to be rotated in either direction, when it stops at half way between its nine and zero positions, and to the closer index position when the drum stops in any position other than half way between nine and zero. The recesses dd, on either side of the lobe 39, receive the follower 4-1 and prevent overtravel of the drum 2, due to inertia, following the lineup.

in the illustrated form of the invention, actuation of the line-up arm 42 is effected by means of an arm 44, which is ailixed to the shaft 43, at the opposite end thereof, and has an actuating lever arm 45 which projects inwardly of the counter frame base 14 and engages a spring do anchored to the base 14 and urging the levers 42, 4-4 to pivot in a counterclockwise direction, as viewed in FiGS. 7-10. The lever arm 45 is arranged to be actedv upon by a solenoid 47, to be described in greater detail,

so that, when the solenoid is actuated, the arms 4-2,

When the solenoid 47 is de-energized,

aorogaoo line-up) which is adapted, when the arm is pivoted in a counterclockwise direction, to engage the drum 23 of the highest order to restrain frictional rotation of the drum. The arm 44, which may be referred to as the braking arm, acts in conjunction with the line-up arm 42, in that the friction pad 43 is held out of contact with the drum until the lineup follower 41 is seated against the circular portion of the cam 33, or in the recesses 42; thereof. Accordingly, braking force is not applied to the drums during the line-up correction. The provision of the braking arm 44 and pad 4% is also highly advantageous in mechanisms adapted for use in military aircraft, for example, where the mechanism may be subjected to substantial vibrations.

Thus, the friction pad 43 engages the highest order drum 23, while the line-up follower ll; engages the cam 38 affixed to the lowest order drum, tending to hold all of the drums in their stopped positions to prevent slight misalignment of the drums, which might otherwise be caused .by vibration of the mechanism and allowed by reason of backlash or the like in the transfer gears. in this respect, it has been found to be satisfactory and expedient to use a single friction pad acting on the drum 23 of the highest order since that drum is subject to the greatest accumulated backlash and is most subject to misalignment caused by vibrations. However, as will be understood, additional brake arms and friction pads may be provided forholding individually some or all of the drums.

Gne of the important features of the invention resides in the provision of an improved rapid reset means for returning the several drums 2il23 to Zero or starting positions at some time after each operational interval. To this end, the rocker frame 3 5, which mounts the spindle shaft 33 carrying the several transfer gears, is mounted for limited pivoting or rocking movement by means of a shaft 4'9 mounted at its ends in the counter frame 13. The rocker frame 34 includes a plurality of reset fingers, one for each of the counter drums li2i3, which extend toward the front of the mechanism and have portions Siiaprojecting generally radially inward toward the drive shaft ii A spring 51 normally acts upon the rocker frame to pivot the frame in a counterclockwise direction, as viewed in F168. 7l0, for example, so that the respective transfer gears 3tl-32 are urged into engagement with the drums 2tl23 and the reset fingers are held spaced away from the drums. A lever arm 52 projects inward from the rocker frame and is arranged for actuating engagement with the arm of a solenoid 53, to be described in more detail, which may be referred to as the reset solenoid. Upon actuation of the solenoid 53, the rocker frame 34 is pivoted in a clockwise direction, so that the transfer gears Sit-32. are disengaged from the drums reset fingers 5% are moved toward the drums so the end portions thereof are in close proximity to the outer surfaces of the drums.

Movement of the frame 34 also carries the transmission gear 3&3 out of engagement with the pinions 25S, 29, so that the drum of the lowest order is disconnected from the drive shaft 1). Accordingly, the drums 2-23 are freely rotatable on the drive shaft 19, except as relative rotation between the drums and shaft may be restrained by the friction of the retaining rings R on the drums. Resetting of the respective drums to zero incx positions is then effected by rotation of the drive shaft 19, advantageously in the same direction as it retates during an operational interval, so that the drums Tad--23 are rotated, by frictional engagement with rings R (fixed on shaft as previously indicated), until reset pins 5d projecting from the surfaces of the respective drums engage the reset fingers Sea. The fingers Stla and pins 54 are so arranged as to stop the drums 2il-Z3 in their zero positions, and rotation of the drive shaft 19 may continue since the shaft can rotate within the stationary drums. Advantageously, the frictional engagement between the drums 2-6-23 and the retaining rings R is such that little slippage of the drums on i116 shaft can occur until the reset pins 54 engage the arms 50. Accordingly all of the drums of the mechanism, regardless of the number thereof, may be reset to zero in not substantially more than a single revolution of the drive shaft The illustrated mechanism is advantageously driven by a governed motor drive, generally indicated by the reference numeral 55, having an output shaft 56 (FIG. 4) to which is ailixed a drive pinion 57. A combined clutch and brake mechanism is provided, which is advantageously of th type described and claimed in the United States Patent No. 2,772,760 of L. I. A. Van Lieshout, issued December 4, 1956 and owned by the assignee of the present application. in general, the clutch mechanism comprises a control plate $8 mounted for pivotal movement about the axis of the output shaft as and carrying a transmission gear 59 which meshes with the drive pinion 57. A spring 6t; engages the plate Sil and also a fixed part of the mechanism framework to urge the plate counterclockwise, as viewed in F168. 3 and 4, to a non-driving position. At desired times, however, the plate 58 may be pivoted clockwise to carry the transmission gear into meshing engagement with a gear fill fixed to or formed inte rally with the shaft 26. Thus, when the plate is pivoted clockwise, the counter mechan... is drh .i ly engaged with the motor unit 55.

The control plate all also carries a brake pad s2, positioned on the side of shaft as generally opposite from the transmission gear 59, so that the brake pad 62 engages the shaft when the control plate is pivoted in a counterclockwise direction. As best shown in P16. 1, the brake pad is located adjacent a knurled portion as of the shaft 26, so that substantial friction is developed between the shaft and brake pad when the spring 6% draws the control plate in a counterclockwise direction.

In the illustrated apparatus, the control plate 53 is ac tuated by means of the solenoid 47, which may be re ferred to as the clutch solenoid. The solenoid 47 has an armature 64 pivoted at one side and having at one end actuating arm portions 65, ss, each having an adjusting screw 67, Mounted on the armature and having a portion extending generally parallel to the actuating arm portion 65' is a yoke so formed of deformable material and having a recess '71; for receiving a pin 7' carried by the control plate 58.

By means of the yoke 69, movements of the armature o are translated to the control plate 53 to move it between its operative positions. And the orientation of the control plate and armature may be precisely adjusted by manipulation of the adjusting screw 67 whereby the disposition cf the yoke 59 with respect to the armature may be varied to a limited extent. The armature 6 5 is normally held away from the core of the solenoid, by the action of the spring so, but is moved toward the core upon energization of the solenoid, to carry the tran mission gear Sh into mesh with the gear of, substantially as shown in PEG. 4.

The second actuating arm portion es of the armature 6d acts, through the adjusting screw ss, upon the lever arm 45 affixed to the brake arm 4 5. Accordingly, vhen the clutch solenoid 4'7 is energized, to connect the counter mechanism to the drive motor unit 55, the lever arm 45 is simultaneously moved to release the drum 23 from the braking pad 43 and to move the line-up follower 41 away from the cam 38.

The reset solenoid 53 has an armature 72 pivoted at one side and carrying an arm 73 which engages an adjusting screw 7 carried by the arm portion of the rocker frame 34. The armature 72 is normally held away from the core of the rest solenoid, against an adjustable stop screw "75, through the action of the rocker frame return spring 5'1 (PlGo. 5, 6). Howe er, when the reset solenoid is energized, the armature "i2 is pivoted toward the solenoid core and the rocker frame is caused to tilt to a position permitting resetting of the drums.

In one advantageous application of the new mechanisrn, the mechanism is housed in a tubular casing 76 provided with a front iiange 77 and a viewing window '73. The mechanism may be used as an interval timer, for example, and in a typical use is adapted to time or measure intervals up to 99.99 seconds, in which case the drum cf the lowest order has index positions corresponding to hundredths of a second, the drum 21 of the next higher order has index positions corresponding to tenths of seconds, and so on. In addition, the lowest order drum 2%) may be calibrated in units of ten, between index positions, the calibrated units r prese" milli seconds. The mechani is, of course, capable of being arranged for use with sm ller or larger time units.

To ready the instrument for timing, the motor unit 55 is energized and set into operation. To start the timing intervals, the clutch solenoid 27 is energized to connect the drive shaft to motor output and set the counting drums in motion. At the end of the timing interval the clutch solenoid 47 is de-energized, which simultaneously disengages the drive shaft from the motor unit and brings the brake pad into engagement with the shat to stop the motion of the drums. Simultaneously with the de-energization of the clutch solenoid 2-7, the shaft 43, mounting the line-up and brake arms 52, 4d is permitted to rotate in a counterclockwise direction by the spring id to effect line-up of the lowest order drum 2%, if necessary, and braking of the highest order drum 23, in sequence. The time may then be read.

in order to reset drums 23 to zero or starting positions, the c. .tch and reset solenoids 47, 533 are energized simultaneously, the motor having been previously set into motion. This causes the drive shaft 19 to rotate. However, since the rocker frame is moved by the reset solenoid to carry the transfer gears 36-32 and the transmission gear out of their operative positions, the drums tend to rotate with the shaft by frictional engagement, until the reset pins 54 engage the reset arms S-ll, at which time the several drums are properly aligned in their zero or starting positions.

A typical circuit for actuating the timing mechanism is illustrated in PEG. 12, in which the motor unit 55 is arranged to be connected to an appropriate source of electrical potental 79 by a switch 89. The switch 8% constitutes a make-ready switch, which sets the motor in operation prior to the timing of an interval. Timing is initiated by closing a switch 81 connected in the energizing circuit of the clutch solenoid Q7, and reset is initiater by closing a double-throw switch 82 having contacts connected in the ener izing circuits of both the clutch and reset solenoids 4",

As one of the important features of the invention, means are provided for properly orienting the several transfer gears 3tl32 during a reset operation so that the gears are appropriately disposed for re-engagement with the reset drums. To this end, the counter frame 13 is provided on its base 14 with a plurality of abutments 83-85 disposed below the transfer gears 3tl32 respectively. The abutments $385 have upper surfaces adapted to engage the transfer gears when the rocker frame 34 is moved to reset position, substantially in the manner indicated in FIG. 10. And the surfaces of the abutments are disposed at such an angle that, when the surfaces are engaged by teeth of the transfergears, the gears are held in a rotational orientation appropriate for re-engagement with the drums, after the drums are reset to zero positions. This is of particular importance in the illustrated form of transfer mechanism, since the respective abutment surfaces prevent rotation of the transfer gears, as might be caused by vibration, for example, so that, upon rte-engagement of the transfer gears with the drums, transfer from one drum to another will take place at a proper time.

In the form of the invention shown in FIG. 13, a modified line-up cam 95 is provided with ten line-up lobes 91, one for each of the index positions of the lowest order drum 92. Accordingly, at the end of a timing or counting interval, when the line-up arm 93 is moved toward the cam, the lowest order drum will be moved to the nearest exact index position. The modified arrangement further facilitates reading of the drums, since all four drums will be properly aligned in their respective windows.

The improved device of the invention is especially adapted for use as a high speed timer, capable of accurate registration, quick reading and rapid reset, and has features rendering it suitable for use in military aircraft, for example, where substantial vibration may be encountered. The improved arrangement for effecting lineup of the drums is especially advantageous where timer readings must be made quickly and accurately, and possibly under conditions of severe stress. Resetting of the timer is practically instantaneous (i.e., about one tenth of a second in the illustrated representative timer), and continued operation of the motor, after the drums reach their respective 0 positions, does not damage the device, as the drive shaft merely continues to rotate within the stationary drums.

it should be understood, however, that the specific forms of the invention herein illustrated and described are intended to be representative only as certain changes may be made therein without departing from the clear teachings of the disclosure. Accordingly, reference should be made to the following appended claims in determining the full scope of the invention.

I claim:

1. A resettable, direct reading counter comprising a drive shaft, external means for rotating said drive shaft, a plurality of counter drums of ascending order rotatively mounted on said drive shaft, indexing transfer means interconnecting lower order drums each to a drum of the next higher order, restraining means engaging the higher order drums for restraining the free rotation thereof on said drive shaft between periodic indexing movements of said higher order drums, said counter drums being adapted for limited frictional rotation on said drive shaft when said drums are unrestrained, drive means connecting said shaft and a drum of lowest order, stop means on said drums, reference means positioned adjacent the drums and movable between operative and inoperative positions and adapted when in operative position to engage said stop means, and reset control means operative when actuated simultaneously to disengage said drive means and said restraining means from said drums and to move said reference means to said operative position, whereby said stop means on said drums are rotated into engagement with said reference means, said external means continuing to rotate said drive shaft when said reset control means is actuated.

2. The counter of claim 1 in which said external means includes a drive motor, a clutch for connecting said motor to said drive shaft, and counting control means for engaging said clutch to effect a drive connection between said motor and shaft, and in which said reset control means includes means for engaging said clutch.

3. The counter of claim 2 which includes a clutch solenoid energizable to engage said clutch, a reset solcnoid energizable to effect disengagement of said drive and transfe means and movement of said reference means to operative position, said counting control comprising means for energizing said clutch solenoid, and said reset control comprising means for simultaneously energizing said clutch and reset solenoids.

4. The counter of claim 1, in which said drive means comprises a pair of pinions supported side by side on said drive shaft, one of said pinions being fixed to said drive shaft while the other pinion is rotatable on the shaft and to the drum of the lowest order, and a transmission gear eng- '15; said pinions, said transfer means comprises transfer ears engaging said drums, and said reset control means includes a rocker frame supporting said transmission and transfer gears and movable to carry said gears into or out or driving positions.

5. The counter of claim 4 including a transfer shaft journaling said transmission and transfer gears, said shaft is mounted on said rocker frame, said reference means are mounted on said rocker frame, and said rocker frame is mounted for pivoting movement about an axis disposed between said transfer shaft and said reference means.

References Cited in the file of this patent UNITED STATES PATENTS 10 Kimball Sept. 14, Olson Sept. 8, Ogden May 13, Schwartz Oct. 29, Bliss Oct. 19, Moody Oct. 3, Dawson Feb. 2,

FOREIGN PATENTS Great Britain Oct. 15, 

